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Master's Degree Thesis
ISRN: BTH-AMT-EX--2013/D11--SE
Supervisors: Andreas Josefsson, BTH Ansel Berghuvud, BTH
Department of Mechanical Engineering
Blekinge Institute of Technology
Karlskrona, Sweden
2013
Jingrui Yang
Rui Duan
Modelling and Simulation of a Bridge interacting with a moving
Vehicle System
Modelling and Simulation of a
bridge interacting with a moving
vehicle system
Jingrui Yang
Rui Duan
Department of Mechanical Engineering
Blekinge Institute of Technology
Karlskrona, Sweden
2012
Thesis submitted for completion of Master of Science in Mechanical
Engineering with emphasis on Structural Mechanics at the Department of
Mechanical Engineering, Blekinge Institute of Technology, Karlskrona,
Sweden.
1
Abstract:
The problem about the vibration of vehicles and bridge is mainly the
problem of coupling vibration between the vehicles dynamic system and
bridge dynamic system. The vehicles running on the bridge at some
speed can make the bridge vibrate, at the same time the vibration of the
bridge will also affect the vibration of the vehicles. This problem with
interaction and mutual effects is the problem of coupling vibration
between vehicles and bridge.
Because its close relation to practical application it is paid extensive
attention by more and more people. In this thesis we construct the
kinetic model of the bridge subsystem and the vehicle subsystem
separately. Then according to the Euler–Bernoulli beam theory [1], mode
superposition method and D’Alambert principle [2] we get the functions
of the two models. In addition we refer to the relationship of the
geometric on the contact point and the static equilibrium conditions to
construct the relation between the equation of the vehicle vibration and
the equation of bridge vibration. Finally we use MATLAB to write the
code according to the Newmark-beta method [3][4] to handle the
coupled equation.
Keywords:
Vehicles-bridge coupling vibration, Dynamic system, D’Alambert
principle, Euler–Bernoulli beam theory, Mode superposition method,
Newmark-beta method.
2
Acknowledgements
From the selection of topic to the finalization of this thesis, our supervisor
Mr.Andreas Josefsson devoted all his attention to each process. Every detail
of the paper was finished with Mr. Andreas Josefsson’s painstaking care.
We would like to express our grateful acknowledgement to our responsible
and humble supervisor of this thesis, Mr. Andreas Josefsson, for helping,
guiding and encouraging us to complete this thesis. We wish to express our
sincere appreciation to him for helping us check out the thesis and suppose
many constructive suggestions. We also would like to thank our friends
providing technical knowledge and valuable advice whenever we needed
during our research work.
At last we would like to thank all of family members for their unconditional
love and understanding. We are also grateful to all of our friends who
support and motivate us to work hard on the thesis.
3
Contents
Acknowledgements 2
Contents 3
1 Notations 4
2 Introduction 6
2.1 Background 6
2.2 Aim and Scope 7
2.3 Structure of the thesis 7
3 Theoretical modelling 9
3.1 Overview 9
3.2 The kinetic model of the vehicle subsystem 10
3.3 The dynamic model of the bridge subsystem 15
3.4 The compatibility conditions 25
3.5 Construction of complete model 28
4 MATLAB simulation 37
4.1 The influence of the speed 40
4.2 The influence of the bridge’s span 44
4.3 The influence of mass of the vehicle 49
4.4 Verification 54
5 Conclusion and future work 58
5.1 Conclusion 58
5.2 Future work 58
5.2.1 Models and calculation method 58
5.2.2 Numerical method 59
6 References 60
Appendices 61
Appendix A: MATLAB scripts 61
4
1 Notations
vM Mass matrix of vehicle model
vC Damping matrix of vehicle model
vK Stiffness matrix of vehicle model
vy Matrix of the degree of freedom of the vehicle
vF Matrix of exciting force of vibration of the vehicle
E Young's modulus
I Moment of inertia Mass of the beam per unit length Damping coefficient per unit length
,F x t Coupled force on the beam
,by x t Beam’s displacement at the contact point
Dirac function
i x Mode of vibration
i t Modal Coordinates
ciy Displacement of the i’th wheel at the contact point
,b iy x t Displacement of bridge at the i’th contact point
5
,ir x t Irregularity of the bridge’s surface at the i’th point
iW Static load of the wheel and the vehicle body gravity of the
wheel undertake
tiK Stiffness of the tire
tiC Damping of the tire
tiy Displacement the wheel’s middle point in the vertical direction
tiy Velocity of the wheel’s middle point in the vertical direction
ciy Displacement in the vertical direction at the contact point
between the tire and the bridge
ciy Velocity in the vertical direction at the contact point between
the tire and the bridge
6
2 Introduction
2.1 Background
In recent decades, with the rapid development of highway communication
around the world, the increasing number of bridges, the emergence of new
bridge’s structure, the increasing bridge span and a significant increase in
vehicle speed, the research of dynamic interaction between vehicles and the
bridge is more and more intensive. The study of vehicle-bridge coupling
vibration focuses on two aspects generally: accurate modeling of coupled
vehicle-bridge system and efficient methods and algorithms for simulating
the dynamic response.
Figure 2.1. A car is running on a bridge
When the vehicles run across the bridge, the pocket weight of the vehicles,
irregularities of the bridge and the acceleration and braking of the vehicle
can lead to excessive vibrations. The vibration will be transferred to the
bridge by tires, which can make the bridge vibrate forcefully. The bridge
will vibrate in vertical, transverse and longitudinal direction, which could
7
lead to damage in the bridge structure. This problem with interaction and
mutual effects is related to coupled vibrations between the vehicle and the
bridge.
Running vehicles on the bridge at high speed can lead to damage to the
bridge structure. At the same time, the vibration of the bridge can affect the
stability, the comfortableness and the safety of the running vehicles.
2.2 Aim and Scope
A major goal of this study is to create a simplified model of a
vehicle-bridge system in MATLAB. The model will then be used to study
the influence of relevant parameters to vehicle-bridge vibrations.
Due to the extensive amount of parameters which affect the vehicle-bridge
coupling vibration, we cannot analyze the influence of all the parameters
comprehensively. Because of a variety of bridges and vehicles, the
theoretical model cannot represent all the bridges and vehicles. Hence, the
following assumptions are made in this thesis:
1) The bridge is modelled as a simply supported beam using Euler–
Bernoulli beam theory.
2) The vehicle is modelled as a lumped parameter system with four degrees
of freedom.
3) Only one vehicle on the bridge is considered in the model.
2.3 Structure of the thesis
A short description of every chapter is presented below to get an overview
of the structure of the thesis.
8
In chapter 3, the main structure of the theoretical model will be illustrated.
Firstly, a simply supported beam is going to be taken as the study project.
According to the Euler–Bernoulli beam theory and mode superposition
method we will build the kinetic model of the bridge subsystem.
Secondly, we will build the double-axle-2D kinetic model of vehicle
subsystem and get the dynamic function referring to the D’Alambert
principle.
Then, we consider these two systems which interact and affect each other as
one system. Base on the relationship of the geometry on the contact point
and the static equilibrium conditions we will construct the relation between
the equation of the vehicle vibration and the equation of bridge vibration.
In chapter 4, the well-known software MATLAB is used to simulate the
model using the Newmark-β method. Simulation results are demonstrated
using different set of parameters.
Finally, chapter 5 summarizes the results and gives some suggestion for
future work.
Appendix contains MATLAB scripts.
9
3 Theoretical modelling
3.1 Overview
The structural form of vehicles is generally complex. From the point of
view of vibration, a vehicle may be seen as complex multi-variant system
consisting of "mass, stiffness and damping". Then different simplified
analysis models are formed. Three kinds of simplified models are
commonly used. They are two degrees of freedom vehicle model with
single axle, double-axle-2D model of vehicle with four degrees of freedom
and three-dimensional model with seven degrees of freedom. In this thesis,
we take the double-axle-2D model of vehicle as an example to carry out the
analysis.
Figure 3.1. The complex structural form of vehicles
As for the bridge we consider it as a simply-supported beam. It is assumed
that the vibration of the bridge is mainly made up by the basic modes of
vibration with lower frequencies. [5] That is to say that the accuracy is high
10
enough to use the lower modes of vibration to describe the vibration of
bridge’s structure. That is the mode superposition method which can
decrease the amount of degrees of freedom of the bridge’s structure. So we
will use this method combined with the Euler-Bernoulli beam theory to get
the kinetic equation in this thesis.
Figure 3.2. A simply-supported bridge
3.2 The kinetic model of the vehicle subsystem
Newton’s law is used to build the 2D model of the double-axle vehicle.
Before building the differential equations we must get some basic
assumptions as follows:
1) The vehicle’s speed is a constant and the vehicle is in linear motion.
2) The vehicle’s tires always close contact with the bridge and no jump
11
occurs.
3) Wheels and body of the vehicle are vibrating with small displacement.
4) Wheels and body are assumed to be rigid bodies with mass, and there is
no internal elastic deformation. They are connected by spring and dampers
to the main structure.
5) Road surface displacement input function impacts on the points of
contact between the tires and the road.
When the double axles vehicle symmetries for the longitudinal
vertical plane altogether and the change of the load roughness below
the left and right wheel is the same, we can consider the vehicle vibrates
in the vertical direction only.
Then we can get the model as follows:
12
Figure 3.3. The model of the double axles vehicle with four degrees of
freedom.
This model has 4 degrees of freedom. The body of the vehicle has two
degrees of the freedom; they are ups and downs of freedom and nod
degrees of freedom separately. The front and back wheel set have a
vertical displacement degree of freedom and separately. Then we
build the kinetic equilibrium function of the vehicle about every degree of
freedom according to the Newton’s law.
Body vibrates up and down:
1 1 1 2 2 2
1 1 1 1 2 2
y ( ) ( )
( ) ( ) 0s s s s t s s t
s s t s s t
m c y y a c y y a
k y y a k y y a
(3.2.1)
Body nodes vibration:
1 1 1 1 2 2 2 2
1 1 1 1 2 2 2 2
( ) ( )
( ) ( ) 0
s s t s s t
s s t s s t
J k a y y a k a y y a
c a y y a c a y y a
(3.2.2)
13
Front axle vibrates in vertical motion:
1 1 1 1 1 1 1 1
1 1 1 1 1 1
( ) ( )
( ) ( ) 0t t s s t s s t
t t c t t c
m y k y y a c y y a
k y y c y y
(3.2.3)
Back axle vibrates in vertical motion:
2 2 2 1 2 2 2 2
2 2 2 2 2 2
( ) ( )
( ) ( ) 0t t s s t s s t
t t c t t c
m y k y y a c y y a
k y y c y y
(3.2.4)
Where,
sm is the mass of the body and the frame of the vehicle.
1tm , 2tm are the mass of the axle between the front and back wheel
set and the tires
1sk , 2sk , 1sc , 2sc are the stiffness and damping between wheel set
and the body of the vehicle.
1tk , 2tk , 1tc , 2tc are the stiffness and damping of the tires
1a , 2a are the displacement from the center of gravity to the back
wheel set or to the front wheel set. The total length is 1 2a a a .
1cy , 2cy are the displacement on the point which the bridge contacts
with the front and back wheel set in the vertical.
1cy , 2cy are the velocity at the point which the bridge contacts with
the front and back wheel set.
14
Transforming the equations into matrix we can get:
v v v v v v vM y C y K y F (3.2.5)
Where,
vM is the mass matrix,
vC is the damping matrix,
vK is the stiffness matrix separately of the model,
vy is the matrix of the degree of freedom of the vehicle,
vF is the matrix of exciting force of vibration of the vehicle.
These matrices are given in Eq. (3.2.6) to Eq. (3.2.10).
1
2
0 0 0
0 0 0
0 0 0
0 0 0
s
vt
t
m
JM
m
m
(3.2.6)
1
2
s
vt
t
y
yy
y
(3.2.7)
15
1 1 1 1
2 2 2 2
0
0v
t c t c
t c t c
Fk y c y
k y c y
(3.2.8)
1 2 1 1 2 2 1 2
2 21 1 2 2 1 1 2 2 1 1 2 2
1 1 1 1 1
2 2 2 2 2
0
0
s s s s s s
s s s s s sv
s s s t
s s s t
k k k a k a k k
k a k a k a k a k a k aK
k k a k k
k k a k k
(3.2.9)
1 2 1 1 2 2 1 2
2 21 1 2 2 1 1 2 2 1 1 2 2
1 1 1 1 1
2 2 2 2 2
0
0
s s s s s s
s s s s s sv
s s s t
s s s t
c c c a c a c c
c a c a c a c a c a c aC
c c a c c
c c a c c
(3.2.10)
3.3 The dynamic model of the bridge subsystem
The dynamic model of the bridge is considered next. To begin with, we
construct the half of the vehicle model running on the bridge.
16
Figure 3.4. The half of the vehicle model in figure 3.3.
Figure 3.5. The model of simply supported beam with the function of
running vehicle.
According to the Euler-Bernoulli beam theory, the governing equation for
flexural vibrations can be written as:
4 2
4 2
, , ,,b b by x t y x t y x t
EI F x t x vtx t t
(3.3.1)
Where,
17
E is Young's modulus of the beam,
I is the moment of inertia of the cross-section,
EI is the flexural rigidity of the beam, is the mass of the beam per unit length, is the damping coefficient per unit length,
,F x t is the coupled force on the beam,
,by x t is the beam’s displacement on the contact point in the
vertical at time t. is the function of Dirac.[6]
The Dirac function has the following characteristics:
0,
,
0,
b
a
t a
f x x t dx f t a t b
t b
(3.3.2)
The function f x is continuous in the closed interval ,a b .
According to the mode superposition method we make,
1
,b i ii
y x t x t
(3.3.3)
Where,
i x is the function of beam mode of vibration,
18
i t is modal Coordinates.
Because the respond of the bridge’s vibration is mainly dominated by some
lower order modes, we need to choose some lower order basic vibration
modes to analyze the response. In this way, we can reduce the number of
degrees of freedom. Hence, we choose the number of modes N to perform
the analysis.
So we can get,
1
( , )N
b i ii
y x t x t
(3.3.4)
According to the condition of normalization of the simply supported beam,
we can get,
sini
i xx A
l
,
sin , 1, 2,3, ,i i
i xx x A i N
l
(3.3.5)
2
0
1l
i x dx (3.3.6)
Then we rewrite it as,
2 2 2 2
0 0
2 2
0
sin
21 cos
12 2
l l
i
l
i xx dx A dx
l
i xll dx
(3.3.7)
19
Where,
2A
l
(3.3.8)
So the function of mode of vibration will become,
2sini
i xx
l l
(3.3.9)
Absolute coordinates can be written as a function of modal coordinates with
1
, tN
b i ii
y x t x
(3.3.10)
to make the superposition analysis.
Then we can get,
4
4
41
, Nb
i ii
y x tx t
x
;
2
21
, Nb
i ii
y x tx t
t
;
1
, Nb
i ii
y x tx t
t
(3.3.11)
Substitute equation (3.3.11) into the function of bridge’s flexural
vibration (3.3.1) we can get that:
20
4
1 1 1
,
N N N
i i i i i ii i i
EI x t x t x t
F x t x vt
(3.3.12)
The next step is to multiply the function of mode of vibration
n x n N on both sides and integrate the equation from 0 to l .
According to the orthogonality of the function of mode of vibration, we can
get:
210
0
0l
ln i i
i n n
i n
x x t dxx dx t i n
(3.3.13)
So we can deduce that,
4
1 10 0
10
0
,
l lN N
n i i n i ii i
l N
n i ii
l
n
x EI x t dx x x t dx
x x t dx
x F x t x vt dx
(3.3.14)
After simplification, it follows that:
21
4 2
0 0
2
0
,
l l
n n n n n
l
n n
n
EI x x dx t x dx t
x dx t
vt F vt t
(3.3.15)
Since,
2
4
0 0
l l
n n nx x dx x dx (3.3.16)
The proof of Eq. (3.3.16) is as follows:
4 3 30
0 0
|l l
ln n n n n nx x dx x x x x dx
2
30
0 0
|l l
ln n n n nx dx x x x x dx
If we want to prove
2
4
0 0
l l
n n nx x dx x dx
We must prove that 30 0| |l l
n n n nx x x x
As we know that 2sinn
n xx
l l
,
So we can get,
22
2cosn
n n xx
l l l
2
2sinn
n n xx
l l l
3
3 2cosn
n n xx
l l l
33
0 0
3
04
2 2| sin cos |
2 1 2sin | 0
2
l ln n
l
n x n n xx x
l l l l l
n n x
l l
2
0 0
3
04
2 2| sin cos |
2 1 2sin | 0
2
l ln n
l
n n x n xx x n
l l l l l
n n x
l l
Hence, we get:
2
4
0 0
l l
n n nx x dx x dx
)
Then we can change equation (3.3.15) into
23
2
2
0 0
2
0
,
l l
n n n n
l
n n
n
EI x dx t x dx t
x dx t
vt F vt t
(3.3.17)
Substitute equation (3.3.6) into equation (3.3.17) we can get
2
0
+ ,l
n n n n nEI x dx t vt F vt t
(3.3.18)
And,
22 2
0 0
4 4 4
5 50
2sin
21 cos2 2 1
2 2
l l
n
l
n n xx dx dx
l l l
n xn n l nl dxl l l
(3.3.19)
Then we assume that
2 ;n n
(3.3.20)
42
2
0
l
n n
EI nEI x dx
l
(3.3.21)
So, the mode equation for the bridge is,
22 ,n n n n n n nF vt t vt (3.3.22)
24
As for the model illustrated figure 3.3.
Because of the different number of contact points, the force will be
different. For the model in the figure3.1, there will be two forces on the
contact points. So the vibration equation of the bridge can be written as
4 2
4 2
2
1
, , ,
,
b b b
i i i ii
y x t y x t y x tEI
x t t
F x t x vt
(3.3.23)
Then, the mode equation for the bridge will be,
21 1 1 2 2 22n n n n n n n nF t F t
(3.3.24)
Where
1
2sinn n
n vtvt
l l
(3.3.25)
2
2sinn n
n vt avt a
l l
(3.3.26)
1
1 0
0
lt
t velse
(3.3.27)
2
1
0
a l at
t v velse
(3.3.28)
25
3.4 The compatibility conditions
The compatibility condition of the displacement is as follows:
, ,ci b i iy y x t r x t (3.4.1)
Where ciy is the displacement of the i’th wheel on the contact point in the
vertical direction, ,b iy x t is the displacement of bridge on the i’th
contact point in the vertical direction, ,ir x t is the irregularity from the
bridge’s surface on the i’th point.
And there are two contact points, so equation (3.4.1) will become:
1 1 11 1 1
11
| , | |
,
c x vt b x vt x vt
N
b i ii
y y x t r x
y vt t r vt vt t r
(3.4.2)
2 2 22 2 2
21
| , | |c x vt a b x vt a x vt a
N
i ii
y y x t r x
vt a t r
(3.4.3)
Where,
1r r vt; 2r r vt a
.
Then we can get
26
1 1 11
|N
c x vt i i i ii
y vt t vt t r
(3.4.4)
2 2 21
|N
c x vt a i i i ii
y vt a t vt a t r
(3.4.5)
When the vehicle is running on the bridge, the force to the bridge from the
i’th wheel is made up of two parts. One is the static load of the wheel and
the vehicle body gravity that wheel undertakes; the other one is the
elasticity from the transformation of the wheel and the damping force
generate from the viscous damping. So the function is
, ( )i i ti ti ci ti ti ciF x t W K y y C y y (3.4.6)
Where,
iW is the static load of the wheel and the vehicle body gravity
of the wheel undertakes,
tiK , tiC is the stiffness and the damping of the tire separately;
tiy , tiy is the displacement and the velocity of the wheel’s middle
in the vertical direction separately;
ciy , ciy is respectively the displacement and velocity in the vertical
direction on the contact point between the tire and the bridge.
So we can get the function of force as follows:
27
1 1 1 1 1 1 1 1 1, k ( )t t c t t cF x t W y y c y y (3.4.7)
2 2 2 2 2 2 2 2 2, k ( )t t c t t cF x t W y y c y y (3.4.8)
Where
21 1s t
aW m m g
a (3.4.9)
12 2s t
aW m m g
a (3.4.10)
According to the equations (3.2.1), (3.2.2), (3.2.3) and (3.2.4) we can get:
21 1 1 1 1 1 1 1
s st t c t t c t t
a m y Jc y y k y y m y
a a
(3.4.11)
12 2 2 2 2 2 2 2
s st t c t t c t t
a m y Jc y y k y y m y
a a
(3.4.12)
Substitute equations (3.4.11) and (3.4.12) into equations (3.4.7) and (3.4.8),
we can get that:
2 21 1 1
1
2 1 12 2 2
,s t t t s s
s t t t s s
a a Jm m g m y m y
F t a a aF x t
F t a a Jm m g m y m y
a a a
(3.4.13)
28
3.5 Construction of complete model
Figure 3.6. The model of double axles vehicle-bridge.
We analyze the situations that the two wheels of vehicle run on and run
down the bridge in consideration of the headway. In our thesis, we will
analyze passing the bridge from three time ranges.
The vehicle starts to run on the bridge, the time range is 0,a
v
;
The vehicle runs on the bridge, the time range is ,a l
v v
;
The vehicle runs down the bridge just on the right edge, the time range is
,l l a
v v
.
Then equations (3.2.3) and (3.2.4) can be written as:
29
1 1 1 1 1 1 1 1
1 1 1 1 1 1 1 1
( ) ( )
( ) ( ) 0t t s s t s s t
t t c t t c
M y k y y a c y y a
k y y c y y
(3.4.14)
2 2 2 1 2 2 2 2
2 2 2 2 2 2 2 2
( ) ( )
( ) ( ) 0t t s s t s s t
t t c t t c
M y k y y a c y y a
k y y c y y
(3.4.15)
According to the compatibility conditions the bridge function (3.3.24) can
be changed to
2 1 1 1 2 2 1 1 2 2
21 1 1 1 2 2 2 2
1 1 1 2 2 2
2
n n n ns s
n t t n t t n n n n n n
n n
a am y J
a a
m y m y
W W
(3.4.16)
We can get the system model of the vehicle-bridge as,
M t Y C t Y K t Y Q t (3.4.17)
Where,
, ,M t C t K t are respectively n 4 orders mass
matrix, damping matrix, stiffness matrix.
Q t is also 4n
orders vector matrix,
Y is 4n orders free vector.
Then we get:
30
1 2 1 2
T
s t t nY y y y (3.4.18)
This is the displacement vector of the system. The matrices are given by:
1
2
2 11 1 1 21 2 11 1 21 211 1 1 21 2 2
2 12 1 1 22 2 12 1 22 212 1 1 22 2 2
2 1 1 1 2 2 1 1 2 21 1 1 2 2 2
0 0 0 0 0 0
0 0 0 0 0 0
0 0 0 0 0 0
0 0 0 0 0 0
1 0 0
0 1 0
0 0 0
s
t
t
s t t
s t t
n n n ns n t n t
m
J
m
m
a am J m mM t a a
a am J m m
a a
a am J m m
a a
1
(3.4.19)
1 2 1 1 2 2 1 22 2
1 1 2 2 1 1 2 2 1 1 2 2
1 1 1 1 1 1 11 1 1 12 1 1 1 1
2 2 2 2 2 2 21 2 2 22 2 2 2 2
1 1
2 2
0 0 0
0 0 0
0
0
0 0 0 0 2 0 0
0 0 0 0 0 2 0
0 0 0 0 0
s s s s s s
s s s s s s
s s s t t t t n
s s s t t t t n
c c c a c a c c
c a c a c a c a c a c a
c c a c c c c c
c c a c c c c cC t
0 0 2 n n
(3.4.20)
31
1 2 1 1 2 2 1 22 2
1 1 2 2 1 1 2 2 1 1 2 2
1 1 1 1 2
2 2 2 2 2
1 11 1 11 1 1 12 1 12 1 1 1 1 1 1
2 21 2
0
0
0 0 0 0
0 0 0 0
0 0 0 0
0 0 0
0 0 0
s s s s s s
s s s s s s
s s s s
s s s t
t t t t t n t n
t t
k k k a k a k k
k a k a k a k a k a k a
k k a k k
k k a k kK t
c k c k c k
c k
21 2 2 22 2 22 2 2 2 2 2 22
12
2
2
0 0
0 0
0 0
t t t n t n
n
c k c k
(3.4.21)
1 1 1 1 1
2 2 2 2 2
11 1 1 21 2 2
12 1 1 22 2 2
1 1 1 2 2 2
0
0
t t
t t
n n
c r k r
c r k rQ t
W W
W W
W W
(3.4.22)
Then according to the conditions we will write the functions for three time
ranges.
32
The first range: the vehicle runs on the bridge (that is to say the front wheel
is on the bridge) then 0
at
v
, so we can get 1 1 , 2 0
.
Then, the coefficients for the function of coupling system (3.4.17) will
become as follows:
1
2
211 11 11 1
212 12 12 1
21 1 1 1
0 0 0 0 0 0
0 0 0 0 0 0
0 0 0 0 0 0
0 0 0 0 0 0
10 1 0 0
10 0 1 0
10 0 0 0 1
s
t
t
s t
s t
s n n n t
m
J
m
m
am J mM t a a
am J m
a a
am J m
a a
(3.4.23)
1 2 1 1 2 2 1 22 2
1 1 2 2 1 1 2 2 1 1 2 2
1 1 1 1 1 1 11 1 12 1 1
2 2 2 2 2
1 1
2 2
0 0 0
0 0 0
0
0 0 0 0
0 0 0 0 2 0 0
0 0 0 0 0 2 0
0 0 0 0 0 0 0 2
s s s s s s
s s s s s s
s s s t t t t n
s s s t
n n
c c c a c a c c
c a c a c a c a c a c a
c c a c c c c c
c c a c cC t
(3.4.24)
33
1 2 1 1 2 2 1 22 2
1 1 2 2 1 1 2 2 1 1 2 2
1 1 1 1 2 1 11 1 11 1 12 1 12 1 1 1 1
2 2 2 2 22
12
2
2
0 0 0
0 0 0
0
0 0 0 0
0 0 0 0 0 0
0 0 0 0 0 0
0 0 0 0 0 0
s s s s s s
s s s s s s
s s s s t t t t t n t n
s s s t
n
k k k a k a k k
k a k a k a k a k a k a
k k a k k c k c k c k
k k a k kK t
(3.4.25)
1 1 1 1
11 1
12 1
1 1
0
0
0t t
n
c r k r
Q tW
W
W
(3.4.26)
The second range: the vehicle passed the bridge(that is to say that two
wheels on the bridge) then a l
tv v
, so we can get 1 2 1 .
Then, the coefficients for the function of coupled system (3.4.17) will
become as follows:
34
1
2
2 11 1 21 11 2111 1 21 2
2 12 1 22 12 2212 1 22 2
2 1 1 2 1 21 1 2 2
0 0 0 0 0 0
0 0 0 0 0 0
0 0 0 0 0 0
0 0 0 0 0 0
1 0 0
0 1 0
0 0 0 1
s
t
t
s t t
s t t
n n n ns n t n t
m
J
m
m
a am J m mM t a a
a am J m m
a a
a am J m m
a a
(3.4.27)
1 2 1 1 2 2 1 22 2
1 1 2 2 1 1 2 2 1 1 2 2
1 1 1 1 1 1 11 1 12 1 1
2 2 2 2 2 2 21 2 22 2 2
1 1
2 2
0 0 0
0 0 0
0
0
0 0 0 0 2 0 0
0 0 0 0 0 2 0
0 0 0 0 0 0 0 2
s s s s s s
s s s s s s
s s s t t t t n
s s s t t t t n
n n
c c c a c a c c
c a c a c a c a c a c a
c c a c c c c c
c c a c c c c cC t
(3.4.28)
1 2 1 1 2 2 1 22 2
1 1 2 2 1 1 2 2 1 1 2 2
1 1 1 1 2 1 11 1 11 1 12 1 12 1 1 1 1
2 2 2 2 2 2 21 2 21 2 22 2 22 2 2 2 2
0 0 0
0 0 0
0
0
0
s s s s s s
s s s s s s
s s s s t t t t t n t n
s s s t t t t t t n t n
k k k a k a k k
k a k a k a k a k a k a
k k a k k c k c k c k
k k a k k c k c k c kK t
2
12
2
2
0 0 0 0 0
0 0 0 0 0 0
0 0 0 0 0 0 n
(3.4.29)
35
1 1 1 1
2 2 2 2
11 1 21 2
12 1 22 2
1 1 2 2
0
0
t t
t t
n n
c r k r
c r k rQ t
W W
W W
W W
(3.4.30)
The third range: the vehicle get down the bridge(that is to say the back
wheel is still on the bridge) then l l a
tv v
, so we can get 1 0 ,
2 1 .
Then, the coefficients for the function of the coupled system (3.4.17) will
become as follows:
1
2
1 21 2121 2
1 22 2222 2
1 2 22 2
0 0 0 0 0 0
0 0 0 0 0 0
0 0 0 0 0 0
0 0 0 0 0 0
0 1 0 0
0 0 1 0
0 0 0 0 1
s
t
t
s t
s t
n ns n t
m
J
m
m
am J mM t a a
am J m
a a
am J m
a a
(3.4.31)
36
1 2 1 1 2 2 1 22 2
1 1 2 2 1 1 2 2 1 1 2 2
1 1 1 1 1
2 2 2 2 2 2 21 2 22 2 2
1 1
2 2
0 0 0
0 0 0
0 0 0 0
0
0 0 0 0 2 0 0
0 0 0 0 0 2 0
0 0 0 0 0 0 0 2
s s s s s s
s s s s s s
s s s t
s s s t t t t n
n n
c c c a c a c c
c a c a c a c a c a c a
c c a c c
c c a c c c c cC t
(3.4.32)
1 2 1 1 2 2 1 22 2
1 1 2 2 1 1 2 2 1 1 2 2
1 1 1 1 2
2 2 2 2 2 2 21 2 21 2 22 2 22 2 2 2 22
12
2
2
0 0 0
0 0 0
0 0 0 0
0
0 0 0 0 0 0
0 0 0 0 0 0
0 0 0 0 0 0
s s s s s s
s s s s s s
s s s s
s s s t t t t t t n t n
n
k k k a k a k k
k a k a k a k a k a k a
k k a k k
k k a k k c k c k c kK t
(3.4.33)
2 2 2 2
21 2
22 2
2 2
0
0
0
t t
n
c r k rQ t
W
W
W
(3.4.34)
37
4 MATLAB simulation
The governing equation for the coupled system was derived in chapter 3. In
this chapter, we will use MATLAB to numerically solve the equation based
on the Newmark-Beta method. A flow diagram for the MATLAB routine is
illustrated below.
39
Table 4.1 and Table 4.2 give the parameters used for the bridge and the
vehicle.
Table 4.1. Bridge parameters.[7]
Tab 4.2. Vehicle parameters.[7]
Item Data Item Data
/sm kg 38500 12 /tk N m 64.28 10
2/J kg m 62.446 10 11 /sc N sm 51.96 10
1 /tm kg 4330 12 /sc N sm 51.96 10
2 /tm kg 4330 11 /tc N sm 49.8 10
11 /sk N m 62.535 10 1
2 /tc N sm 49.8 10
12 /sk N m 62.535 10 1 /a m 4.2
11 /tk N m 64.28 10 2 /a m 4.2
1/v km h 40, 80, 120, 160
So we write the MATLAB code using the flow diagram and the parameters
The span
length
( )l m
The mass of bridge
per unit length
( / )kg m
The flexural rigidity
of the bridge 2( )EI N m
The damping
coefficient per unit
length
16 9360 102.05 10 0.025
40
given above. Simulation results are shown in the following chapters where
the influence of 1) vehicle speed, 2) bridge and 3) vehicle mass, is
demonstrated.
4.1 The influence of the speed
The simulated bridge displacement is shown in Fig. 4.1 to 4.2 for vehicle
speed 40 80, 120 and 160 km/h.
Figure 4.1 The mid-span dynamic displacement of bridge in different
speeds.
41
Figure 4.2 The vertical displacement of bridge at contact points for
different speeds (the upper figure is the first contact point, the lower figure
is second contact point).
From figure 4.1, we can get that the maximum of the mid-span
displacement will increase with the increasing speed of the vehicle,
although the relationship is not linear. We also can get that the maximum of
the mid-span displacement coming out is not when the vehicle runs on the
middle of the bridge. It happens on the left or right of the mid-span.
42
Figure 4.2 shows us that the maximum displacement of the bridge happens
when the vehicle locates in the front or back of the mid-span. With
increasing speed, the maximum displacement will increase. But, when the
speed is at some value, the value of the maximum displacement will be
smaller than that in the front speeds. This is related to the resonance of the
vehicle-bridge structures in combination with the speed of the vehicle.
The high frequency fluctuation is a result from the vehicle-bridge coupled
vibration. On the contrary, when the vehicle runs at high speed, the time for
the high frequency fluctuation is not enough to act sufficiently before the
vehicle gets down the bridge. Then the fluctuation of the curve will be
weak.
Fig 4.3 to 4.5 gives the displacement at the vehicle structure.
Figure 4.3 The vertical displacement of vehicle in different speeds.
44
Figure 4.5 The vertical displacement of vehicle’s axle in different speeds
(the upper figure is for front axle, the lower figure is back axle).
4.2 The influence of the bridge’s span
The analysis is repeated with a longer bridge span using the parameters
shown below:
45
Table 4.3. Parameters of bridge. [8]
The span
length
( )l m
The mass of bridge
per unit length
( / )kg m
The flexural rigidity
of the bridge 2( )EI N m
The damping
coefficient per unit
length
50 32840 115.28 10 0.029
The result (for different speeds) can be seen in Fig. 4.6 to 4.10.
Figure 4.6 The mid-span dynamic displacement of bridge in different
speeds.
46
Figure 4.7 The vertical displacement of bridge lie in contact point by
different speeds (the upper figure is the first contact point, the lower figure
is for second contact point).
47
Figure 4.8 The vertical displacement of vehicle in different speeds.
Figure 4.9 The node angular displacement of vehicle in different speeds.
48
Figure 4.10 The vertical displacement of vehicle’s axle in different speeds
(the upper figure is front axle, the lower figure is for back axle).
By comparing figure 4.1 with figure 4.6, we can see that a bigger span leads
to a larger mid-span displacement of the bridge under the condition that the
vehicle runs at the same speed.
By comparing figure 4.4 with figure 4.9 we can get that as for the
small-span bridge especially when the length of the vehicle equals nearly
the length of the bridge, the node of the vehicle body has an obvious effect
49
on the response of the bridge.
4.3 The influence of mass of the vehicle
The difference when using a different set of parameters for the vehicle is
studied next.. The table below shows the new parameters.
Table 4.4. Parameters of vehicle.[8]
Item Data Item Data
/sm kg 15090 12 /tk N m 47.5 10
2/J kg m 53871 11 /sc N sm 41.2 10
1 /tm kg 190 12 /sc N sm 43.0 10
2 /tm kg 190 11 /tc N sm 600
11 /sk N m 53.7 10 1
2 /tc N sm 600
12 /sk N m 62.06 10 1 /a m 2.97
11 /tk N m 45.35 10 2 /a m 1.18
1/v km h 40, 80, 120, 160
We take the same span of 4.2 and run the MATLAB code. The result can be
seen in figure 4.11 to 4.15.
51
Figure 4.12 The vertical displacement of bridge lie in contact point by
different speeds (the upper figure is the first contact point, the lower figure
is for second contact point).
52
Figure 4.13 The vertical displacement of vehicle in different speeds.
Figure 4.14 The node angular displacement of vehicle in different speeds.
53
Figure 4.15 The vertical displacement of vehicle’s axle in different speeds
(the upper figure is for front axle, the lower figure is for back axle).
By comparing figure 4.11 with figure 4.6, we can get that the heavier mass
of the vehicle can make the fluctuation of the mid-span displacement of the
bridge more severe.
By comparing figure 4.12 with figure 4.7 we can get that the heavier the
mass of the vehicle is, the bigger the maximum displacement of the bridge
will be, under the condition that the vehicle runs at the same speed.
54
From figure 4.8 to 4.10 and figure 4.13 to 4.15, we can get that different
masses can affect the vehicle body vibrations significantly. As demonstrated
with these simulations, a vehicle running on a bridge with a heavy load can
lead to a strong dynamic interaction between the bridge and the vehicle
system.
4.4 Verification
A static calculation is carried out in order to verify the simulated
displacement.
We will verify the mid-span displacement of the bridge.
According to the Euler-Bernoulli beam theory and in the situation that the
point load is on the middle of the bridge we can get that:
24
4 Lx
EI
P
dx
d
(4.4.1)
Integrate it 4 times, we can get
13
3
2c
Lx
EI
P
dx
d
(4.4.2)
3221
2
2222
1cxcx
cLx
Lx
EI
P
dx
d
(4.4.3)
432231
3
26226
1cxcx
cx
cLx
Lx
EI
Px
(4.4.4)
And we also know that the boundary conditions are as follows:
55
0 0x
0x L
2
020xx
2
20x Lx
(4.4.5)
Then we can get that
3
4
4
10 0 0 (4.4.6)
6 2 2
0 sin 0 0
P L Lc
EI
c ce x if x
002
02
00 221
ccc
LL
EI
P (4.4.7)
EI
PcLc
LL
LL
EI
P
2220 11
1
(4.4.8)
LcLcL
LL
LEI
P3
31
1
3
6226
10
(4.4.9)
LcLEI
PL
EI
P3
33
12480
(4.4.10)
3
2
16c
EI
PL
(4.4.11)
So, we can get:
2262226
1
2 3
3
1
3L
cLcL
xLL
EI
PLx
(4.4.12)
EI
PL
EI
PLLx
32962
33
(4.4.13)
56
EI
PLLx
482
3
(4.4.14)
We take the “Table 4.1. Bridge parameters” and “Tab 4.2. Vehicle
parameters” as an example
These are parameters we will use:
1 2
10 2
m 38500
=m 4330
9.8 /
16
2.05 10 m
s
t t
kg
m kg
g N kg
L m
EI N
Substitute these parameters in the equation above we can get:
m0.00162
Lx
We then compare this static displacement with the simulated displacement
in figure 4.16.
57
Figure 4.16 The mid-span dynamic displacement of bridge in different
speeds.
From this figure we can also find that when the vehicle runs to the centre of
the bridge the simulated displacement is around 0.0012 to 0.0015m. Hence,
it is verified that the simulated displacement produced by the model is
reasonable.
58
5 Conclusion and future work
5.1 Conclusion
In this work, we construct the models of the bridge and vehicle separately
based on the theory of vehicle-bridge coupled vibration. The models were
then connected by suing geometric relationships force equilibrium
conditions to construct the relation between the equation of the vehicle
vibration and the equation of bridge vibration. Finally, we use MATLAB to
handle the coupled problem based on the Newmark-β method. The
MATLAB code was then used to study the influence of various parameters.
As the simulation results show, the speed of the vehicle has a significant
effect on the dynamic response of the bridge. In general, the faster the
speed is, the bigger the maximum dynamic displacement is.
Also, when the span of the bridge is bigger, the maximum of displacement
will become bigger at the condition that the vehicle runs at the same speed.
When the mass of the vehicle increases, the maximum dynamic
displacement will increase significantly under the condition that the
vehicle’s speed is the same, and the span of the bridge is the same. And,
vehicles with different masses also affect the safety and comfort of the
drivers and passengers significantly.
5.2 Future work
5.2.1 Models and calculation method
In this thesis, we use two-dimensional models of the vehicle and bridge
system. The model and calculation method for the bridge is simplified to a
59
beam model , but for arch bridges with larger span and other bridges a
three-dimensional FEM-model could be more suitable . It is also possible to
extend the model of the vehicle. In this thesis, we take the two-axle lumped
vehicle model as an example to analyze the coupled vibration. A more
general FEM model could be considered for this purpose.
5.2.2 Numerical method
The Newmark-β method was used in this work to solve the governing
equations of motion. In this way, we lack the comparison between different
numerical methods. Other numerical methods, which are perhaps more
suitable for the studied problem, should be examined in future work.
60
6 References
[1] Wikipedia. (accessed October 2012). Euler–Bernoulli beam theory.
http://en.wikipedia.org/wiki/Euler%E2%80%93Bernoulli_beam_theory.
[2] Wikipedia. (accessed October 2012). D'Alembert's principle.
http://en.wikipedia.org/wiki/D'Alembert's_principle.
[3] Wikipedia. (accessed October 2012). Newmark-beta method.
http://en.wikipedia.org/wiki/Newmark-beta_method.
[4] WANG Hai-bo, CHEN Bo-wang, YU Zhi-wu. (2008). A Simplified
Numerical Integration Format of Newmark-β Method for Structural
Dynamic Equations. Journal of Sichuan University (Engineering Science
Edition), Vol.40 No.3, May 2008. Article ID: 1009-3087(2008)03-0047-06
[5] Clough, R.W.; Penzien, Joseph. (1993). Dynamics of Structures (2nd
Edition). ISBN-13: 978-0-07-011394-7.
[6] Xia He, Zhang Nan. (2002). Dynamic Interaction of Vehicles and
Structures. ISBN: 9787030100320
[7] XIAO Xin-biao, SHEN Huo-ming. (2004). Comparison of Three
Models for Vehicle-Bridge Coupled Vibration Analysis. Journal of
Southwest Jiaotong University. Vol.39 No.2 Apr. 2004. Article
ID:0258-2724(2004) 02-0172-04
[8] WANG Jiejun, ZHANG Wei,WU Weixiang. (2005). Analysis of
Dynamic Responses of Simply Supported Girder Bridge under Heavy
Moving Vehicles. Central South Highway Engineering. Vol.30 No.2
Jun,2005. Article ID: 1002-1205(2005)02-0055-03
61
Appendices
Appendix A: MATLAB scripts
main.m
clc
clear
close all
% the main program
global rou EI l mu
l=16;
mode=30; %input('how many mode shape ')
N=mode+4;
%parameters:
ms=38500;
mt1=4330;
mt2=4330;
J=2.446e6;
ks1=2.535e6;
ks2=2.535e6;
cs1=1.96e5;
cs2=1.96e5;
kt1=4.28e6;
kt2=4.28e6
ct1=9.8e4;
ct2=9.8e4;
a1=4.2;
a2=4.2;
62
a=a1+a2;
global rou EI l mu
rou=9360;
EI=2.05e10;
mu=0.025;
%%
velocity=40*1000/3600; % the speed of the car
T=(l+a)/velocity;
dt=0.000001*T;
t=0:dt:T;
t=t';
x=t*velocity;
level=1; %level:A=1,B=2.C=3......
nl=4;
NN=1000;
nu=5;
r=irregularity(level,NN,nl,nu,x); %level:A=1,B=2......
r_dot=(r(2:length(r))-r(1:length(r)-1))/dt;
A=zeros(N,length(t));
V=zeros(N,length(t));
X=zeros(N,length(t));
Q=zeros(N,length(t));
A0=zeros(N,1);
V0=zeros(N,1);
X0=zeros(N,1);
for jjj=1:length(t)
63
if t(jjj)*velocity<l;
delta1=1;
irr1=r(jjj);
irr_dot1=r_dot(jjj);
else delta1=0;
irr1=0;
irr_dot1=0;
end
if t(jjj)*velocity<l+a&t(jjj)*velocity>a;
delta2=1;
irr2=r(floor((t(jjj)*velocity-a)/dt/velocity)+1);
irr_dot2=r_dot(floor((t(jjj)*velocity-a)/dt/velocity)+1);
else delta2=0;
irr2=0;
irr_dot2=0;
end
[M,C,K]=MCK(ms,mt1,mt2,J,ks1,ks2,cs1,cs2,kt1,kt2,ct1,ct2,a1,a2,N,delta1,delta2,t(jjj),ve
locity);
Q=force(ct1,ct2,kt1,kt2,ms,a1,a2,mt1,mt2,irr1,irr2,irr_dot1,irr_dot2,velocity,t(jjj),delta1,de
lta2,N);
A0=M\(Q-C*V0-K*X0);
X1=X0+V0*dt+1/2*A0*dt^2;
V1=V0+A0*dt;
A1=M\(Q-C*V1-K*X1);
error1=1;
while error1>0.0001;
64
X2=X0+V0*dt+(1/2-1/4)*A0*dt^2+1/4*A1*dt^2;
V2=V0+(1-1/2)*A0*dt+1/2*A1*dt;
A2=M\(Q-C*V2-K*X2);
error1=sum(abs(abs(A2)-abs(A1)))/sum(abs(A1));
A1=A2;
V1=V2;
X1=X2;
end
X0=X1;
V0=V1;
A0=A1;
X(:,jjj)=X0;
V(:,jjj)=V0;
A(:,jjj)=A0;
end
save('D:\MATLABDATA\differentvelocity\A40','A');
save('D:\MATLABDATA\differentvelocity\V40','V');
save('D:\MATLABDATA\differentvelocity\X40','X');
save('D:\MATLABDATA\differentvelocity\Q40','Q');
MCK.m
function
[M,C,K]=MCK(ms,mt1,mt2,J,ks1,ks2,cs1,cs2,kt1,kt2,ct1,ct2,a1,a2,N,delta1,delta2,t,velocity)
%% N is the dimemsions of the matrix
global rou EI l mu
% rou is the constant like density ????
65
%% M matrix
M=zeros(N,N);
M1=[ms,J,mt1,mt2];
M1=diag(M1);
a=a1+a2;
for n=1:N-4
phi1n=sqrt(2/rou/l)*sin(n*pi*t*velocity/l);
phi2n=sqrt(2/rou/l)*sin(n*pi*(t*velocity-a)/l);
M(n+4,1)=(a1*phi1n*delta1+a2*phi2n*delta2)*ms/a;
M(n+4,2)=(phi1n*delta1-phi2n*delta2)*J/a;
M(n+4,3)=phi1n*delta1*mt1;
M(n+4,4)=phi2n*delta2*mt2;
end
M2=ones(N-4,1);
M2=diag(M2);
M(1:4,1:4)=M1;
M(5:N,5:N)=M2;
%% C matrix
C=zeros(N,N);
for n=1:N-4
phi1n=sqrt(2/rou/l)*sin(n*pi*t*velocity/l);
phi2n=sqrt(2/rou/l)*sin(n*pi*(t*velocity-a)/l);
C(3,n+4)=-ct1*phi1n*delta1;
C(4,n+4)=-ct2*phi2n*delta2;
end
C1=[cs1+cs2,cs1*a1-cs2*a2,-cs1,-cs2;...
cs1*a1-cs2*a2,cs1*a1^2+cs2*a2^2,-cs1*a1,cs2*a2;...
-cs1,-cs1*a1,cs1+ct1,0;...
66
-cs2,cs2*a2,0,cs2+ct2];
C2=mu/rou*diag(ones(N-4,1));
C(1:4,1:4)=C1;
C(5:N,5:N)=C2;
%% K matrix
K=zeros(N,N);
omega_n_2=zeros(1,N-4);
for n=1:N-4
phi1n=sqrt(2/rou/l)*sin(n*pi*t*velocity/l);
phi2n=sqrt(2/rou/l)*sin(n*pi*(t*velocity-a)/l);
phi1n_dot=n*pi/l*sqrt(2/rou/l)*cos(n*pi*t*velocity/l);
phi2n_dot=n*pi/l*sqrt(2/rou/l)*cos(n*pi*(t*velocity-a)/l);
K(3,n+4)=(-ct1*phi1n_dot-kt1*phi1n)*delta1;
K(4,n+4)=(-ct2*phi2n_dot-kt2*phi2n)*delta2;
omega_n_2(1,n)=EI/rou*(n*pi/l)^4;
end
K1=[ks1+ks2,ks1*a1-ks2*a2,-ks1,-ks2;...
ks1*a1-ks2*a2,ks1*a1^2+ks2*a2^2,-ks1*a1,ks2*a2;...
-ks1,-ks1*a1,ks1+kt1,0;...
-ks2,ks2*a2,0,ks2+kt2];
K2=diag(omega_n_2);
K(1:4,1:4)=K1;
K(5:N,5:N)=K2;
67
angulardisplacement.m
clc
clear
close all
l=16;
a1=4.2;
a2=4.2;
a=a1+a2;
rou=9360;
velocity=40*1000/3600; % the speed of the car
T=(l+a)/velocity;
dt=0.000001*T;
t=0:dt:T;
load('D:\MATLABDATA\differentvelocity\X40')
%% Change X V A for displacement, velocity and accelraction
[rows1,columns1]=size(X);
X_location=X(2,:);
rou=9360;
plot(t*velocity,X_location,'r-','LineWidth',1)
hold on
l=16;
a1=4.2;
a2=4.2;
a=a1+a2;
rou=9360;
velocity=80*1000/3600; % the speed of the car
T=(l+a)/velocity;
dt=0.000001*T;
68
t=0:dt:T;
load('D:\MATLABDATA\differentvelocity\X80')
[rows1,columns1]=size(X);
X_location=X(2,:);
rou=9360;
plot(t*velocity,X_location,'b--','LineWidth',1)
hold on
l=16;
a1=4.2;
a2=4.2;
a=a1+a2;
rou=9360;
velocity=120*1000/3600; % the speed of the car
T=(l+a)/velocity;
dt=0.000001*T;
t=0:dt:T;
load('D:\MATLABDATA\differentvelocity\X120')
[rows1,columns1]=size(X);
X_location=X(2,:);
rou=9360;
plot(t*velocity,X_location,'g-.','LineWidth',1)
hold on
l=16;
a1=4.2;
a2=4.2;
a=a1+a2;
rou=9360;
velocity=160*1000/3600; % the speed of the car
T=(l+a)/velocity;
dt=0.000001*T;
69
t=0:dt:T;
load('D:\MATLABDATA\differentvelocity\X160')
[rows1,columns1]=size(X);
X_location=X(2,:);
rou=9360;
plot(t*velocity,X_location,'k:','LineWidth',1)
xlabel('The location of vehicle (m)')
ylabel('The node angular displacement of vehicle (m)')
title(' The node angular displacement of vehicle in different speeds')
legend('40km/h','80km/h','120km/h','160km/h','location','north')
axles.m
clc
clear
close all
l=16;
a1=4.2;
a2=4.2;
a=a1+a2;
rou=9360;
velocity=40*1000/3600; % the speed of the car
T=(l+a)/velocity;
dt=0.000001*T;
t=0:dt:T;
load('D:\MATLABDATA\differentvelocity\X40')
%% Change X V A for displacement, velocity and accelraction
[rows1,columns1]=size(X);
X_location=X(3,:);
rou=9360;
plot(t*velocity,X_location,'r-','LineWidth',1)
70
hold on
l=16;
a1=4.2;
a2=4.2;
a=a1+a2;
rou=9360;
velocity=80*1000/3600; % the speed of the car
T=(l+a)/velocity;
dt=0.000001*T;
t=0:dt:T;
load('D:\MATLABDATA\differentvelocity\X80')
[rows1,columns1]=size(X);
X_location=X(3,:);
rou=9360;
plot(t*velocity,X_location,'b--','LineWidth',1)
hold on
l=16;
a1=4.2;
a2=4.2;
a=a1+a2;
rou=9360;
velocity=120*1000/3600; % the speed of the car
T=(l+a)/velocity;
dt=0.000001*T;
t=0:dt:T;
load('D:\MATLABDATA\differentvelocity\X120')
[rows1,columns1]=size(X);
X_location=X(3,:);
rou=9360;
plot(t*velocity,X_location,'g-.','LineWidth',1)
71
hold on
l=16;
a1=4.2;
a2=4.2;
a=a1+a2;
rou=9360;
velocity=160*1000/3600; % the speed of the car
T=(l+a)/velocity;
dt=0.000001*T;
t=0:dt:T;
load('D:\MATLABDATA\differentvelocity\X160')
[rows1,columns1]=size(X);
X_location=X(3,:);
rou=9360;
plot(t*velocity,X_location,'k:','LineWidth',1)
xlabel('The location of vehicle (m)')
ylabel('The vertical displacement of the front axle (m)')
title('The vertical displacement of axles in different speeds')
legend('40km/h','80km/h','120km/h','160km/h','location','north')
bridge_XVA.m
function X=bridge_XVA(modes,L,xG,mp)
%NM the mode shape % L the length of the bridge % xG the location
NM=length(modes);
X=zeros(size(xG));
for i=1:NM
X=X+sqrt(2/mp/L)*sin(i*pi*xG/L)*modes(i);
end
72
contactnew1.m
clc
clear
close all
l=50;
a1=2.97;
a2=1.18;
a=a1+a2;
rou=32840;
velocity=40*1000/3600; % the speed of the car
T=(l+a)/velocity;
dt=0.000001*T;
t=0:dt:T;
load('D:\MATLABDATA\differentvelocity3\X40')
%% Change X V A for displacement, velocity and accelraction
[rows1,columns1]=size(X);
X_location=zeros(columns1,1);
rou=32840;
X_contact1=zeros(length(t),1);
X_contact2=zeros(length(t),1);
XXG1=zeros(length(t),1);
XXG2=zeros(length(t),1);
for jjj=1:length(t)
if t(jjj)*velocity<l;
deltal1=1;
else deltal1=0;
end
73
if t(jjj)*velocity<l+a&t(jjj)*velocity>a;
deltal2=1;
else deltal2=0;
end
xG1=t(jjj)*velocity;
xG2=t(jjj)*velocity-a;
X_contact1(jjj)=bridge_XVA(X(5:rows1,jjj),l,xG1*deltal1,rou)*deltal1;
X_contact2(jjj)=bridge_XVA(X(5:rows1,jjj),l,xG2*deltal2,rou)*deltal2;
XXG1(jjj)=xG1;
XXG2(jjj)=xG2;
end
plot(XXG1,X_contact1,'r-','LineWidth',1)
hold on
l=50;
a1=2.97;
a2=1.18;
a=a1+a2;
rou=32840;
velocity=80*1000/3600; % the speed of the car
T=(l+a)/velocity;
dt=0.000001*T;
t=0:dt:T;
load('D:\MATLABDATA\differentvelocity3\X80')
[rows1,columns1]=size(X);
X_location=zeros(columns1,1);
rou=32840;
X_contact1=zeros(length(t),1);
74
X_contact2=zeros(length(t),1);
XXG1=zeros(length(t),1);
XXG2=zeros(length(t),1);
for jjj=1:length(t)
if t(jjj)*velocity<l;
deltal1=1;
else deltal1=0;
end
if t(jjj)*velocity<l+a&t(jjj)*velocity>a;
deltal2=1;
else deltal2=0;
end
xG1=t(jjj)*velocity;
xG2=t(jjj)*velocity-a;
X_contact1(jjj)=bridge_XVA(X(5:rows1,jjj),l,xG1*deltal1,rou)*deltal1;
X_contact2(jjj)=bridge_XVA(X(5:rows1,jjj),l,xG2*deltal2,rou)*deltal2;
XXG1(jjj)=xG1;
XXG2(jjj)=xG2;
end
plot(XXG1,X_contact1,'b--','LineWidth',1)
hold on
l=50;
a1=2.97;
a2=1.18;
a=a1+a2;
rou=32840;
velocity=120*1000/3600; % the speed of the car
T=(l+a)/velocity;
75
dt=0.000001*T;
t=0:dt:T;
load('D:\MATLABDATA\differentvelocity3\X120')
[rows1,columns1]=size(X);
X_location=zeros(columns1,1);
rou=32840;
X_contact1=zeros(length(t),1);
X_contact2=zeros(length(t),1);
XXG1=zeros(length(t),1);
XXG2=zeros(length(t),1);
for jjj=1:length(t)
if t(jjj)*velocity<l;
deltal1=1;
else deltal1=0;
end
if t(jjj)*velocity<l+a&t(jjj)*velocity>a;
deltal2=1;
else deltal2=0;
end
xG1=t(jjj)*velocity;
xG2=t(jjj)*velocity-a;
X_contact1(jjj)=bridge_XVA(X(5:rows1,jjj),l,xG1*deltal1,rou)*deltal1;
X_contact2(jjj)=bridge_XVA(X(5:rows1,jjj),l,xG2*deltal2,rou)*deltal2;
XXG1(jjj)=xG1;
XXG2(jjj)=xG2;
end
plot(XXG1,X_contact1,'g-.','LineWidth',1)
76
hold on
l=50;
a1=2.97;
a2=1.18;
a=a1+a2;
rou=32840;
velocity=160*1000/3600; % the speed of the car
T=(l+a)/velocity;
dt=0.000001*T;
t=0:dt:T;
load('D:\MATLABDATA\differentvelocity3\X160')
[rows1,columns1]=size(X);
X_location=zeros(columns1,1);
rou=32840;
X_contact1=zeros(length(t),1);
X_contact2=zeros(length(t),1);
XXG1=zeros(length(t),1);
XXG2=zeros(length(t),1);
for jjj=1:length(t)
if t(jjj)*velocity<l;
deltal1=1;
else deltal1=0;
end
if t(jjj)*velocity<l+a&t(jjj)*velocity>a;
deltal2=1;
else deltal2=0;
end
xG1=t(jjj)*velocity;
xG2=t(jjj)*velocity-a;
77
X_contact1(jjj)=bridge_XVA(X(5:rows1,jjj),l,xG1*deltal1,rou)*deltal1;
X_contact2(jjj)=bridge_XVA(X(5:rows1,jjj),l,xG2*deltal2,rou)*deltal2;
XXG1(jjj)=xG1;
XXG2(jjj)=xG2;
end
plot(XXG1,X_contact1,'k:','LineWidth',1)
xlabel('The location of the contact point (m)')
ylabel('The dynamic displacement of bridge on the first contact point (m)')
title('The dynamic displacement of bridge on the first contact point in different speeds')
legend('40km/h','80km/h','120km/h','160km/h','location','north')
contactnew2.m
clc
clear
close all
l=50;
a1=2.97;
a2=1.18;
a=a1+a2;
rou=32840;
velocity=40*1000/3600; % the speed of the car
T=(l+a)/velocity;
dt=0.000001*T;
t=0:dt:T;
load('D:\MATLABDATA\differentvelocity3\X40')
%% Change X V A for displacement, velocity and accelraction
[rows1,columns1]=size(X);
78
X_location=zeros(columns1,1);
rou=32840;
X_contact1=zeros(length(t),1);
X_contact2=zeros(length(t),1);
XXG1=zeros(length(t),1);
XXG2=zeros(length(t),1);
for jjj=1:length(t)
if t(jjj)*velocity<l;
deltal1=1;
else deltal1=0;
end
if t(jjj)*velocity<l+a&t(jjj)*velocity>a;
deltal2=1;
else deltal2=0;
end
xG1=t(jjj)*velocity;
xG2=t(jjj)*velocity-a;
X_contact1(jjj)=bridge_XVA(X(5:rows1,jjj),l,xG1*deltal1,rou)*deltal1;
X_contact2(jjj)=bridge_XVA(X(5:rows1,jjj),l,xG2*deltal2,rou)*deltal2;
XXG1(jjj)=xG1;
XXG2(jjj)=xG2;
end
plot(XXG2,X_contact2,'r-','LineWidth',1)
hold on
l=50;
a1=2.97;
a2=1.18;
79
a=a1+a2;
rou=32840;
velocity=80*1000/3600; % the speed of the car
T=(l+a)/velocity;
dt=0.000001*T;
t=0:dt:T;
load('D:\MATLABDATA\differentvelocity3\X80')
[rows1,columns1]=size(X);
X_location=zeros(columns1,1);
rou=32840;
X_contact1=zeros(length(t),1);
X_contact2=zeros(length(t),1);
XXG1=zeros(length(t),1);
XXG2=zeros(length(t),1);
for jjj=1:length(t)
if t(jjj)*velocity<l;
deltal1=1;
else deltal1=0;
end
if t(jjj)*velocity<l+a&t(jjj)*velocity>a;
deltal2=1;
else deltal2=0;
end
xG1=t(jjj)*velocity;
xG2=t(jjj)*velocity-a;
X_contact1(jjj)=bridge_XVA(X(5:rows1,jjj),l,xG1*deltal1,rou)*deltal1;
X_contact2(jjj)=bridge_XVA(X(5:rows1,jjj),l,xG2*deltal2,rou)*deltal2;
XXG1(jjj)=xG1;
80
XXG2(jjj)=xG2;
end
plot(XXG2,X_contact2,'b--','LineWidth',1)
hold on
l=50;
a1=2.97;
a2=1.18;
a=a1+a2;
rou=32840;
velocity=120*1000/3600; % the speed of the car
T=(l+a)/velocity;
dt=0.000001*T;
t=0:dt:T;
load('D:\MATLABDATA\differentvelocity3\X120')
[rows1,columns1]=size(X);
X_location=zeros(columns1,1);
rou=32840;
X_contact1=zeros(length(t),1);
X_contact2=zeros(length(t),1);
XXG1=zeros(length(t),1);
XXG2=zeros(length(t),1);
for jjj=1:length(t)
if t(jjj)*velocity<l;
deltal1=1;
else deltal1=0;
end
if t(jjj)*velocity<l+a&t(jjj)*velocity>a;
81
deltal2=1;
else deltal2=0;
end
xG1=t(jjj)*velocity;
xG2=t(jjj)*velocity-a;
X_contact1(jjj)=bridge_XVA(X(5:rows1,jjj),l,xG1*deltal1,rou)*deltal1;
X_contact2(jjj)=bridge_XVA(X(5:rows1,jjj),l,xG2*deltal2,rou)*deltal2;
XXG1(jjj)=xG1;
XXG2(jjj)=xG2;
end
plot(XXG2,X_contact2,'g-.','LineWidth',1)
hold on
l=50;
a1=2.97;
a2=1.18;
a=a1+a2;
rou=32840;
velocity=160*1000/3600; % the speed of the car
T=(l+a)/velocity;
dt=0.000001*T;
t=0:dt:T;
load('D:\MATLABDATA\differentvelocity3\X160')
[rows1,columns1]=size(X);
X_location=zeros(columns1,1);
rou=32840;
X_contact1=zeros(length(t),1);
X_contact2=zeros(length(t),1);
XXG1=zeros(length(t),1);
82
XXG2=zeros(length(t),1);
for jjj=1:length(t)
if t(jjj)*velocity<l;
deltal1=1;
else deltal1=0;
end
if t(jjj)*velocity<l+a&t(jjj)*velocity>a;
deltal2=1;
else deltal2=0;
end
xG1=t(jjj)*velocity;
xG2=t(jjj)*velocity-a;
X_contact1(jjj)=bridge_XVA(X(5:rows1,jjj),l,xG1*deltal1,rou)*deltal1;
X_contact2(jjj)=bridge_XVA(X(5:rows1,jjj),l,xG2*deltal2,rou)*deltal2;
XXG1(jjj)=xG1;
XXG2(jjj)=xG2;
end
plot(XXG2,X_contact2,'k:','LineWidth',1)
xlabel('The location of the contact point (m)')
ylabel('The dynamic displacement of bridge on the second contact point (m)')
title('The dynamic displacement of bridge on the second contact point in different speeds')
legend('40km/h','80km/h','120km/h','160km/h','location','north')
force.m
function
Q=force(ct1,ct2,kt1,kt2,ms,a1,a2,mt1,mt2,r1,r2,r_dot1,r_dot2,velocity,t,delta1,delta2,N)
global rou l
a=a1+a2;
83
g=9.876;
W1=(ms*a2/a+mt1)*g;
W2=(ms*a1/a+mt2)*g;
Q=zeros(N,1);
Q(3)=(ct1*r_dot1+kt1*r1)*delta1;
Q(4)=(ct2*r_dot2+kt2*r2)*delta2;
for n=1:N-4;
phi1n=sqrt(2/rou/l)*sin(n*pi*t*velocity/l);
phi2n=sqrt(2/rou/l)*sin(n*pi*(t*velocity-a)/l);
Q(n+4)=-(phi1n*W1*delta1+phi2n*W2*delta2);
end
irregularity.m
function r=irregularity(level,N,nl,nu,x)
Gdn0=4^(level+1)*10^(-6);
detal_n=(nu-nl)/N;
n0=0.1;
r=zeros(length(x),1);
W=2;
for k=1:N
nk=nl+(k-0.5)*detal_n;
Gdn=Gdn0*(nk/n0)^(-W);
Ank=sqrt(4*Gdn*detal_n);
r=r+Ank*cos(2*pi*nk*x+rand(1)*2*pi);
end
School of Engineering, Department of Mechanical Engineering Blekinge Institute of Technology SE-371 79 Karlskrona, SWEDEN
Telephone: E-mail:
+46 455-38 50 00 [email protected]